Pumping units for cyclonic elevator

ABSTRACT

Coaxial pumping units for cylindrical cyclonic elevator tubes in which a manifold circumscribing the latter for supplying fluid under pressure thereto has communication therewith via an annular transition ring provided with a plurality of circumferentially spaced jet orifices set at inwardly and circumferentially directed compound angles for ejecting vortically directed jets of fluid under pressure through the tubular elevator to effect transportation of comminuted and/or fluid material through such tubes.

United States Patent [191 Bruno 1 PUMPING UNITS FOR CYCLONIC ELEVATOR[76] Inventor: Anthony I. Bruno, 4333 Dawson Ave., San Diego, Calif. 92115 [22] Filed: July 26, 1973 121] App]. No.: 382,823

Related US. Application Data [63] Continuation of Ser. No. 155,750, June23, 1971,

abandoned.

[52] US. Cl 417/171, 417/163, 37/61, Y 302/15, 302/58 [51] Int. Cl F04f5/42 [58] Field of Search 37/61, 62; 417/194, 171,

[56] References Cited UNITED STATES PATENTS 140,017 6/1873 Cram 302/25640,463 1/1900 Gildea 302/25 UX [111 3,857,651 1 Dec. 31, 1974 1,341,0105/1920 Cartwright 302/25 UX 1,819,346 8/1931 To1man,.1r.... 37/61 UX1,914,991 6/1933 Coghlan 302/25 X 2,191,424 2/1940 Cardinal 37/61 UX2,673,125 3/1954 Squire, Jr 302/25 3,301,606 l/1967 Bruno 37/61 UX3,389,938 6/1968 302/14 3,672,790 6/1972 White et al. 417/108 PrimaryExaminer--C1ifford D. Crowder [57] ABSTRACT Coaxial pumping units forcylindrical cyclonic elevator tubes in which a manifold circumscribingthe latter for supplying fluid under pressure thereto has communicationtherewith via an annular transition ring provided with a plurality ofcircumferentially spaced jet orifices set at inwardly andcircumferentially directed compound angles for ejecting vorticallydirected jets of fluid under pressure through the tubular elevator toeffect transportation of comminuted and/or fluid material through suchtubes.'

5 Claims, 15 Drawing Figures PATENTED HERB 1 I974 SHEET 10F 4 INVEN OR-l. BRUNO fi ANTHONY PATENTEU B5173 3 857. 651

' sum 3 OF 4 INVENTORI ANTHONY I. BRUNO PATENTEUUEB3 1 1 3,857; 651

SHEET H 0F 4 INVENTORI ANTHONY I. BRUNO PUMPING UNITS FOR CYCLONICELEVATOR This is a continuation of application Ser. No. 155,750 filedJune 23, 1971, now abandoned.

BACKGROUND OF INVENTION In the transportation of dry comminuted orpowdered materials from one place'to another, for instance, cottonresulting from a ginning operation, wheat and rice hulls resulting fromprocesses adapted to remove such hulls, and the transportation ofpowdered cement from kilns to storage areas,.it is necessary to confinethe material being transported so that it'is not disseminated into theatmosphere, while simultaneously propelling the material to move alongthe conveyor. Heretofore, various types of mechanical conveying meanshave been utilized, but in most instances these mechanical conveyingmeans have disadvantages which either precluded their use or renderedsuch use prohibitively expensive. For instance, most mechanicalconveying means require elaborate support structures and drivingmechanisms for moving the material from one point to another. In otherinstances, movement of the metal is ineffectively controlled, causingcostly stopages which interrupt operations. Accordingly, it is one ofthe principle objects of this invention to provide a transportationmeans for wet or dry material that utilizes in general a tubularconveyor having smooth interior surfaces in conjunction with a fluidcushion interposed between the walls of the conveyor tube and thematerial being conveyed, while imparting to the material being conveyeda propulsive force causing it to move through the tubular conveyor.

In conveying apparatuses in which liquids are transported, such as wateror oil, it has been the practice to impose a positive pressure on theinlet end of the conveyor with the pressure thus being transmitted tothe body of material being moved. So far as is known, no attempt hasheretofore been made to provide a layer of a different type fluidbetween the liquid being transported and the pipeline or tube withinwhich it is contained. Accordingly, it is another object of theinvention to provide for the transportation of a liquid medium throughan elongated tubular conveyor by the method of providing a cushioninglayer of a different fluid between the liquid being conveyed and thecontainer through which it passes, while simultaneously causing saidcushioning layer of fluid to impart to the liquid being conveyed 'aforward motion.

In the realm of underwater dredging, it has been customary practice touse clam shell or drag line and bucket type equipment which physicallygouges the bottom of the ocean, lake or river, lifts the material thusconfined within the "clam shell" or bucket up through the water anddeposits the material in an appropriate barge or on shore. This methodof underwater dredging loosens the mud and silt forming the bottom andcauses wide dispersion of fine solids in suspension, thus causing agreat deal-of pollution of the surrounding body of water. Accordingly,it is a still further object of this invention to provide a dredgingapparatus which effectively picks up loose material lying on the bottomof a body of water, loosens hard material so that it too may be lifted,and effectively prevents dis persion of solids in suspension beyond theimmediate area being dredged.

Heretofore, mechanical means have had to be used to effect loosening ofthe hard material forming the bottom of a body of water. Suction typedredges have been used to lift loose material, but there has been no wayother than through use of mechanical means to effect a loosening of hardmaterials so that these too could be lifted. It is one of the objects ofthe present invention to provide an apparatus and method which throughthe utilization of pneumatic and hydraulic means effects a loosening andlifting motion to the soil forming the bottom of a body of water.

Instances will of course be encountered when pneumatic and hydraulicmeans are insufficient to effect loosening of hard packed soil.Accordingly, in these instances, additional mechanical means may benecessary, working in conjunction with the pneumatic and hydraulicmeans, to initially break up the soil and cause it to be conveyed away.

BRIEF SUMMARY OF INVENTION In terms of broad inclusion, the apparatus ofthe invention comprises a hollow conveyor tube provided at one end witha unitary pumping assembly adapted to discharge into the interior of thehollow conveyor tube in a predetermined pattern of a multiplicity ofstreams of a fluid under high pressure, the direction and force ofdischarge of said jets of high pressure fluid into the conveyor tubebeing controlled to simultaneously provide a cushion of such fluidbetween the material to be conveyed andthe inner wall of the tubularconveyor, and impart to the material to be conveyed a forward motion. Inone aspect of the invention, a plurality of separate pumping unitsarespaced axially along the conveyor tube for operation in series. Theangle of inclination of discharge of the fluid medium into the interiorof the conveyor is varied'from a relatively sharp angle at the inceptionor first pump unit to a relatively shallow angle at the last pump unit.Additionally, the interior of the tubular conveyor in the areaimmediately adjacent the discharge of the fluid medium into the tubularconveyor is formed to provide Venturi action to increase the velocity ofthe fluids and entrained solid material moving through the tubularconveyor.

DESCRIPTION OF DRAWINGS FIG. 1 is a perspective view illustrating theapparatus of the invention mounted on a barge. The dredging action ofthe inverted generally conical body of water immediately below thedredging apparatus is illustrated schematically.

FIG. 2 is a schematic view illustrating three successive pumping unitsand illustrating the angular relationship of discharge of a fluid mediuminto the interior of the tubular conveyor at successive stages along theconveyor from the three pumping units.

FIG. 3 is a vertical cross-sectional view through three of the assembledpumping heads.

FIG. 4 is a horizontal cross-sectional view taken in the plane indicatedby the line 4-4 in FIG. 3.

FIG. 5 is a horizontal crosssectional view taken in the plane indicatedby the line 5-S in FIG. 3.

FIG. 6 is an enlarged fragmentary vertical crosssectional view taken inthe plane indicated by the line' 6-6 in FIG. 5.

FIG. 7 is a plan view partly in horizontal section illustrating thepattern of fluid discharge bores in one of the pump assemblies.

FIG. 8 is an enlarged fragmentary vertical crosssectional view takenthrough the 35th orifice in the first stage pumping unit, the view beingtaken in the plane indicated by the line 88 in FIG. 7.

FIG. 9 is an enlarged vertical cross-sectional view similar to FIG. 8,taken through the 35th orificein the second-stage pumpingunit.

FIG. 10 is an enlarged fragmentary cross-sectional view similar to FIGS.8 and 9, illustrating a fragmentary section through the 35th orifice ofthe third stage pumping unit. 7

FIG. 11 is a full-size fragmentary plan view illustrating by'way ofexample, the'compound inclination of the axis of each of the fluiddispensing orifices of each pumping unit.

FIG. 12 is a vertical. cross-sectional view taken in the plane indicatedby the line l2--l2 in FIG. 1 1, the plane of section being coincidentwith and including the axis of the orifice.

FIG. 13 is a vertical cross sectional view taken in the plane indicatedby the'line 13-13 in FIG. 12.

FIG. 14 is an elevational view illustrating a second embodiment of theinvention which includes apparatus I associated with the pumping headsoperative to loosen and break up solid terrain in close proximity to thepumping heads. I

FIG. 15 is a horizontal cross-sectional view taken in the planeindicated by the line 15-15 in FIG. 14.

DESCRIPTION OF PREFERRED EMBODIMENT In termsof greater detail, thematerial moving and 1 transporting apparatus of the invention will bedescribed in connection with its use for underwater dredging purposes.It should be understood that use in such an underwater environment isbeing illustrated merely by way of example and not by way of limitation,it being believed that an underwater environment preseats the most andgreatest .difficulties.

Referring to FIG. 1, the apparatus of the invention is designatedgenerally by the numeral 2, and is shown mounted on an appropriate barge3 equipped witha crane 4 operable to elevate or lower the apparatus intothe water into spaced relation with the bottom under the body of water.The dredging assembly 2 is arranged coaxially of a hollow, cylindricalconveyor tube T which is connected to appropriate tubular extensions 6,supported on conventional buoys or floats 7. Air compressor means 8 areprovided for pumping air under pressure to the dredging assembly.

As illustrated in FIG. 1, the compressor unit 8 is connected by anappropirate pipe or hose 9 to each of the manifolds l2, l3 and 14associated with each of the pumping units 16, 17 and 18, respectively.For purposes of this description, the pumping units 18, 17 and 16respectively, will sometimes'be referred to as the first, second andthird pumping or dredging stages.

Referring to FIG. 3, it will there be seen that each of the three stagesof the dredging apparatus includes a transition ring 21 normal to theaxis of the conveyor tube T and having a top surface 22,.a lower surface23, an inner periphery 24 and an outer periphery 26. The inner periphery24 of the transition ring preferably has an inside diametersubstantially equal to the inside diameter of the hollow conveyor tubeto which the dredging units are detachably secured as will hereinafterbe' explained. Each of the transition rings is annular in configurationand is provided with a multiplicity of generally axially extending jetorifices in the form of bores 27, conveniently 45 in number so that thebores are spaced approximately 8.3 from one another around thetransition ring.

Welded to the upper surface 22 of each transition ring adjacent itsouter periphery is a generally conical section 28 which merges with atubular cylindrical section 29 as shown. The inner diameter of thecylindrical section 29 is preferably equal to the inner diameter of thetransition ring. Welded to the lower surface 23 of the transition ringis a downwardly extending tubular section 31, having a diametersubstantially equal to the diameter of the cylindrical section 29, butprojecting in the opposite direction therefrom. As shown, the innerperipheral surface 24 of the transition ring andthe inner periphery ofthe cylindrical section 31 are flush, so that the transition from thecylindrical section 31 through the transition ring is a smooth one.

Sealingly interposed between the outer peripheries 26 of each of thetransition rings and the outer peripheries of the associated cylindricalsections 31 attached thereto, preferably by welding,are theaforementioned manifolds 12, 13 and 14, respectively.

As depicted in FIGS. 8, 9 and 10, each manifold 14, 13 and 12,respectively, comprises an annular tube circumscribing the respectivetransition ring 21 of each pumping unit l8, l7 and 16, respectively.Such annular tube, 14, 13 or 12, as the case may be, is ofC shape incross section, i.e., radially of such annular tube. providing an uppercrown 25 and a lower tail 30 spaced vertically a distance diametricallyits C shape slightly greater than the vertical thickness, bottom to top,of the transition ring 21. The upper crown end 25 of the C shapedannular tube is secured, as by welding to the outer periphery of theflared open end of the conical section 28 and outer periphery 26 on thetransition ring of the pumping unit and the lower tail end 30 of the Cshaped annular tube extends horizontally toward and is secured bywelding to the outer periphery of the downwardly extending tubularsection 31 attached to the bottomof the transition ring 21 to therebyprovide an annular chamber 33 circumscribing the bottom and Y outerperiphery of the transition ring. The manifolds are appropriatelydetachably connected in parallel to the downwardly extendinghigh-pressure supply pipe or hose 9 as illustrated in FIG. 1, thusconnecting the chambers within the manifolds to the source ofhighpressure fluid.

Relating bores 27 illustrated in FIG. 3 to the plan view of such boresillustrated in FIG. 7 and the enlarged fragmentary verticalcross-sectional view of a single bore 27 illustrated in FIG. 8, andreferring also to the cross-sectional illustrations of these bores inFIGS. 11 through 13, it will be seen that each bore 27 is provided withan inlet end 34 and an outlet end 36. In general, the inlet ends 34 ofall of the bores 27 formed in each transition ring 21 are spaced apredetermined equal distance from the central axis of the ring, whilethe outlet ends 36 of the bores vary in their spacing from the centralaxis of the ring. This variation in spacing of the outlet ends of thebores results in a different angularity of the axis of each of the boreswith respect to the central axis of the ring that contains them. Thisdifference in angularity of the different bores is illustrated intabular form below in Table I.

In addition to being variably spaced from the central axis of the ringcontaining the bores, the outlet ends 36 of the bores are variablyspaced circumferentially about the ring, thus causing a difference inangularity or inclination of the axes of the bores in a circumferentialdirection. It will thus be seen that each of the bores 27 is located inthe transition ring so that collectively the inlet ends 34 of all of thebores lie on a common circle the center of which coincides with thecentral axis of the ring. The outlet ends 36 of the bores, however, varyin radial spacing from the central axis of the ring to form a spiralgradually diminishing pattern of outlet ends 36 in the direction of flowon the top surface 22 of the associated transition ring. The outlet ends36 of the bores also vary in spacing along the spiral by virtue of thevariable inclination of the axes of the bores as they progresscircumferentially about the transition ring within which they areformed. It will thus be seen that the several bores in the transitionring each have their axes set to extend inwardly and circumferentiallyat compound angles. Moreover, that charging each manifold chamber 33with a highpressure fluid will immediately result in the discharge offorty-five separate high-pressure jets'or streams inclined toward thecentral axis of the ring and also inclined circumferentially about thering at such compound angles as to impart combined inwardly directed anda circumferentially directed vertical forces on any fluid,fluid-entrained solid material, or dry material that passes through thetransition ring.

For the first stage unit 18, illustrated in FIGS. 1 and 3, the number ofbores is preferably 45, proportioned to have a diameter of approximately3/8 inch. The degree of inclination of the axis of each of the boreswith rcspcct to the central axis of the ring within which it iscontained (FIG. 13), together with the degree (C) of inclination of theaxis of each of the bores in a circumferential direction is indicated bythe following ta bles in which the bores are listed as orifices bynumber from 1 to 45:

TABLE I TABLE II TABLE III FIRST STAGE SECOND STAGE THIRD STAGE OrificeOrifice Orifice No. ti" c" No. b c No. i l 8 3O I 9 2O I9 9 l4 2 8 30 29 2O l0-l8 8 l3 3 8 29 3 9 20 19-26 7 l2 4 9 29 4 9 l9 27-35 6 ll 5 9 285 9 l9 36-45 5 IO 6 9 28 6 I9 7 I0 27 7 l0 l8 8 IO 27 8 l0 l8 9 I0 26 9l0 l3 10 ll 26 l0 l0 [7 ll ll 25 ll l0 l7 12 ll 25 l2 l0 l7 l3 I2 24 I3IO l6 l4 I2 24 I4 I0 l6 l5 I2 23 15 IO l6 l6 I2 23 l6 l0 l5 l7 I3 22 I7l0 l5 l8 I3 22 l8 l0 l5 l9 13 2| 19 IO 14 20 I4 21 20 l0 l4 Zl I4 2O 2]l0 I4 22 I5 20 22 l0 I3 23 l5 I9 23 IO I3 24 l6 I9 24 10 I3 '25 l6 I8 25l0 I2 26 l7 I8 26 l0 I2 27 l7 I7 27 IO l2 28 l8 17 28 IO ll 29 I8 16 29IO ll 30 l9 I6 30 I0 ll 3! l9 [5 3I ID ID 32 20 I5 32 10 IO 33 20 I4 33l0 I0 34 21 I4 34 I0 9 -Continued TABLE I TABLE II TABLE III FIRST STAGESECOND STAGE THIRD STAGEv 35 21 I3 35 10 9 36 22 I3 36 IO 9 38 23 I2 38IO 8 39 23 ll 39 IO 8 4D 24 IO 40 I0 8 42 25 8 42 1O 8 r 43 26 7 43 IO 8From Table I above it will be seen that starting with orifice No. l thedegree of inclination of the axis of this .bore with respect to thecentral axis of the ring in which it is formed is 8, whereas the degreeof inclination of this bore in a circumferential direction is 30.Thereafter, with respect to the first stage, each of the successivebores is inclined at a greater angle radially inward and at lesserangles of inclination circumferentially progressively in the directionof the diminishing spiral of outlets 36 about the transition ring 21 tothe degrees indicated in Table I.

Referring to FIGS. 1 and 3, and specifically to the second stagedredging unit 17, with respect to the bores 27 in this second stage,orifice No. 35 of which is illustrated in FIG. 9, it will be seen thatwhile the same number of bores has been provided in the transition ring,the degree of inclination of the separate bores with respect to thecentral axis of the ring containing the bores varies from 9 for orificeNo. l to 10 for orifice No.45. It will thus be seen that there is asignificant difference between the angularity of bores 27 in the secondstage with bores 27 in the first stage, especially with respect toorifice Nos. 13 et seq. in the first stage dredging unit. Thus, in thefirst stage, the angularity of the bores starting with orifice No. 13range from 12 for orifice or bore No. 13, to a maximum of 27 for orificeNo. 45.

In like manners in the second stage, the preferred inclination (C) ofthe axis of each of the bores in a circumferential direction ranges from20 for orifice No. l to 8 for orifice No. 45. This is in contrast withthe pattern of inclination of the bores in the first stage in which themaximum inclination for orifice No. l was 30 and the minimum inclination5. From a functional point of view, it will thus be seen that in generalthe propulsive effect and rotative moment imposed on a stream ofmaterial, liquid or otherwise, by the pattern of first stage bores willbe greater than the effect of the pattern of bores in the second stage,the second stage being effective and working on a body of liquid orother material that is already moving as a result of the propulsiveeffect of high pressure fluid jetted through the first stage bores. Theinclination of each of the bores for the second stage is illustrated inTable 2 above.

Referring to the third dredging or pumping stage 16 I of the apparatus,with specific reference to FIG. 10, the inclination (if) of the axis ofthe bores 27 with respect to the central axis of ring 21 vary between amaximum of 9 and minimum of 5. On the other hand, the circumferentialinclination (C) of the bores varies between a maximum of 14 and aminimum of 10. Table 3 above sets forth the specific values ofinclination for the respective bores.

Comparing FIGS. 8 through 10, it will be seen that maximum propulsiveforce and a maximum rotative moment on the fluid or material beingtransported is secured by action of the first stage 18. As thetransported fluid or material gains momentum in an axial directionthrough the tubular conveyor, the high pressure fluid jetted from thecircumferentially inclined bores. also imparts a rotary moment thatstarts the materialspiraling as it progresses axially through theconveyor tube T. By the time the material reaches the second stage, ithas already begun to move in both an axially and circumferentialdirection. The second stage thus imparts an added boost to the charge ofmaterial passing through the conveyor, and passes the material on to thethird stage in which the axial component of force exerted by theseparate jets on the material passing therethrough is maximal and therotative force is minimal. It will thus be seen that as many stages asis necessary may be arranged in series to propel the material over longdistances, for instance up to several miles.

Referring to FIG. 3, it will be noted that the conical sections 28 nextadjacent the respective transition rings 21, merge smoothly with therelatively smaller diameter cylindrical sections 29. The upper endportion 37 of each cylindrical section 29 is provided with acircumferential groove 38 (FIG. 6) adapted to receive a clamp ring 39proportioned to provide a flange 41 and 42 locking respectivelyingrooves 38 and 43. The groove 43 is formed adjacent the end portion'44of tubular section 31 projecting downwardly from the second stage 17. Itwill thus be seenthat the first and second stages are clamped rigidlytogether so that their adjacent edges are in abutting relationship. Toinsure a fluidtight connection between the cylindrical members 29 and31, a deformable gasket material 46 is interposed between the outersurfaces of the end portions 29 and 44 and the clamp ring 39 so thatwhen the clamp is tightly bound about the cylindrical members, thedeformable gasket material seals the union between the cylindricalmembers. This construction is illustrated best in FIGS. and 6. As shown,the relatively smaller diametered cylindrical sections 29 and 31constitute venturi means disposed between the successive conicalsections 28 of units 16, 17 and 18.

It will thus be seen that the clamp means illustrated in FIGS. 5 and 6may be utilized to clamp as many stages together in series as may beneeded for a particular application. Thus, under some circumstances, itmay be sufficient to provide only a single or a first stage pumping ordredging unit. Under other circumstances, it may be necessary to utilizea plurality of pumping units. It should also be understood that thethree different stages may be arranged in a different sequence from thatillustrated. Thus, the unit 16 here designated as the third stage may besubstituted for the first stage,

etc.

In the use of the dredging apparatus, it will sometimes occur that thesoil or material with which the dredging unit is used is so hard thatthe erosive force imposed on the material is not sufficient to loosenthe material. Accordingly, as illustrated in FIGS. 14 and 15, thepumping and dredging apparatus of the invention is adapted to be used inconjunction with a mechanically driven excavating unit mounted on thelower end of the pumping and dredging unit, and adapted to engage suchsolid material and soil and effect loosening and scarifying thereof sothat the pumping and dredging unit may act upon it.

As illustrated in FIG. 14, such mechanical scarifying apparatuscomprises a support plate 51 having a central aperture, the innerperiphery 52 of which is appropriately welded about the exterior of thelower most pumping unit between the first and second stages. The outerperiphery of the support plate 51 is provided with appropriate aperturesto receive cap screws 53. Detachably secured to the mounting plate 51 isa radially outwardly extending mounting plate 54 the inner end 56 ofwhich is provided with a series of apertures to receive the cap screws53 and is arcuate in form to conform to the configuration of the annularsupport plate 51. Preferably, to effect a balance, a second mountingplate 54' of similar construction is provided on the right hand side asviewed in FIG. 14 and is detachably secured to the support plate 51 inlike manner. Both mounting plates 54 and '54 are provided with centrallydisposed apertures 56 for purposes which will hereafter be explained.Each side of the mechanical scraifying apparatus is alike and thereforelike reference numerals are applied to like parts thereof.

Axially spaced below the mounting plates 54 and 54', and in generalalignment therewith extending radially outwardly in opposite directionsfrom the central axis of the pumping unitis a second mounting plate 57or 57' as the case may be..This plate is provided with a centralaperture 58 adapted to fit around the outer periphery of tubularextension 59 of a bracket 61 having a generally J-shaped cross sectionincluding a return bend 62 adapted to be welded to the underside of theleft and right mounting plates 57-57. The tubular extension 59 of theJ-shaped section is appropriately secured to the inner peripheralsurface 24 of the lowermost transition ring 21. To provide detachabilityof the excavating apparatus from the pumping unit, the J- shaped bracket61 may be secured by appropriate screws threaded into the associatedtransition ring of the pumping unit. Alternatively, where a. permanentinstallation is desired, the apparatus may be welded directly to thepumping unit.

'As illustrated in FIG. 14, each radially projecting portion of thesecond mounting plate 57 is provided with a generally centrally disposedaperture 63 spaced from the central axis 64 of the pumping unit. Theapertures 63 are proportioned to snugly receive the outer periphery of acylindrical mounting tube 64 the upper end 66 of which is appropriatelywelded to the underside of associated mounting plates 54 or 54', whilethe lower most end 67 of the mounting tube is closed by a closure plate68 supported in a manner which will hereinafter be explained. Within themounting tube, there are provided appropriate lugs 69 adapted todetachably support a bearing assembly 71 adjacent the upper end of themounting tube, and a bearing assembly 72 adjacent the lower end of themounting tube.

The bearing assemblies appropriately rotatably sup-' port a centrallydisposed drive shaft 73 secured against axial displacement in thebearing assemblies by appropriate collars 74. The upper end of the driveshaft is splined at 76 for appropriate engagement to the drive shaft ordrive pinion (not shown) of an appropriate drive unit designatedgenerally by the numeral 77 in FIGS. 14 and 15 and preferably comprisinga multiplicity of hydraulic motors 78 arranged circumferentially aboutthe drive shaft and mounted on an appropriate support frame 79. Ahoisting ring 81 is provided to facilitate placement of the motorassembly on the mounting plate 54, and appropriate securing means (notshown) are provided to secure the motor assembly in position.Conventionally, such hydraulic motors are driven by appropriatehydraulic fluid channeled through conventional high pressure hoses orconduit (not shown) in the usual manner.

Below the closure plate 68, the drive shaft 73 continues in a section 82the lowermost end of which is conically pointed as at 83. Intermediatethe conical point 83 and the closure plate 68, the drive shaft extension82 is provided with radially extending spokes 84 welded at their inner(upper) ends to the drive shaft extension immediately below the closureplate 68. The spokes are inclined downwardly, as illustrated best inFIG. 14, the outer ends of the spokes being disposed within the innerperiphery of the circular rim 86 having about its outer periphery andradially projecting therefrom a plurality of blades 87 each of which isprovided with a leading edge 88 sharpened to effect cutting of anymaterial with which it makes contact, and being inclined upwardly asillustrated in FIG. 14 so that upon rotation the blades 87 tend todrive-loosened material upward in the direction of the pumpingmechanism. Preferably, there are at least eight such blades providedaround the outer periphery of the rim. Such blades are particularlyuseful for scarifying the vertical banks of a sea or river channel thatmight be encountered by the dredging apparatus.

To effectively loosen and scarify the soil immediately below thedredging apparatus, the rim 86 is provided with downwardly extendingblades 89, the downwardly projecting blades varying in height asindicated. There are preferably approximately 12 such downwardlyextending blades.

It may occur that the nature of the terrain or soil into which thedredging apparatus must dig is of a nature to require a constantdownward pressure on the part of the dredging apparatus over and aboveits own weight. To effectively provide such additional downwardlydirected pressure, the lower end portion 91 of the drive shaft extension82 is provided with spiral lands 92 as shown, proportioned to increasein diameter from the conical point 83 so that once the conical point haspenetrated the soil, the lands 92 immediately begin to draw the driveshaft and associated structure downwardly into firm engagement with thesoil.

It should be understood that while only two such excavating units havebeen shown associated with the pumping head, as many excavating unitsmay be supported on the pumping assembly as is consistent with theclearances required for their operation. Thus, for a symetricalstructure, two additional excavating units could be associated with thetwo shown to provide a total of four, the separate excavating unitslying at 90 intervals around the central axis of the apparatus.

Having thus described the invention, what is claimed to be novel andsought to be protected by letters patent is as follows:

I claim:

1. Pumping units for a cylindrical cyclonic elevator tube in which fluidunder pressure from a source thereof has communication therewith via aplurality of circumferentially spaced jet orifices set at inwardlydirected angles gradually increasing from a minimum angle with respectto the central axis of the tube of not less than 5 and circumferentiallydirected compound angles of inclination correspondingly graduallydecreasing in inclination from a maximum angle circumferentially forejecting vortically directed jets of fluid under pressure upwardlythrough the cyclonic elevator to effect transportation of comminutedand/or fluid material through such tube; each said pumping unitcomprising in combination:

a. a tubular section having an axial length substantially equal to itsradius;

b. a frusto-conical section having its truncated end secured to thelower end of said tubular section and its flared sides extendingtherefrom a distance comparable to the length of said tubular section;

c. a transition ring having its outer periphery secured to the flaredopen end on said conical section and an inner periphery of a diametercomparable to said tubular section and having such circumferentiallyspaced jet orifices formed therebetween from the bottom to the uppersurface thereof such that the inwardly directed angle of the minimumangle of such jet orifices converges with a projection of the innersurface of the flared side walls of said conical section, slightly abovethe truncated end of said conical section;

d. an intermediate tubular section having a diameter equal to that ofsaid tubular section and secured opposite thereto to the bottom surfaceof said transition ring with its internal periphery flush with the innerperiphery of said transition ring;

e. a manifold for each of said pumping units comprising an annular tube,of C-shaped cross section radially thereof and of a diameter verticallyfrom its annular crown to its annular tail slightly greater than thevertical thickness, top to bottom, of said transition ring and havingits annular crown secured to the outer periphery of the flared end ofsaid conical section at its plane of connection to said transition ringand having its annular tail extending horizontally toward saidintermediate tubular section and secured thereto for providing anannular chamber about the outer exposed periphery and bottom surface ofsaid transition ring;

f. and means for communicating said annular chamber with the source offluid under pressure.

2. The combination in accordance with claim 1 in which the plurality ofspaced jet orifices formed in said transition ring of said pumping unithave their inlet ends on the manifold side of the transition ringarranged equidistant from center of the latter and their outlet ends onthe opposite side of such ring, beginning with a first such jet orificeshaving its axis inclined at a minimum angle radially inward of suchring, arranged in groups progressivelydecreasing in distance radially ofsaid transition ring in a spiral pattern toward the axis of the latterwhereby said bores have their axes disposed in progressively decreasingangles toward center in such spiral pattern.

3. The combination in accordance with claim 1 in which therfirst namedjet orifice in said transition ring has its outlet end ofi'set relativeto its inlet end at a greater distance circumferentially than suchoffset relation of the inlet to outlet of the other orifices of saidplurality thereof and in which successive groups of orifices' thereofhave the offset relation of their inlet and outlet gradually diminishingin a circumferential direcposed at compound angles ranging from 8 to 27radially and correspondingly 30 to 5 circumferentially;

b. a second, intermediate stage having the circumferentially spacedorifices in its transition ring disposed at compound angles ranging from9 to 10 radially and correspondingly 20 to 8 circumferentially; and

c. an innermost stage having the circumferentially spaced orifices inits transition ring disposed at compound angles ranging from 9 to 5radially and correspondingly 14 to l0 circumferentially.

Patent No.

3 ,857 ,651 Dated December 31 1974 Inventor (s) Anthony I. Bruno It iscertified that error appears in the above-identified patent and thatsaid Letters Patent are hereby corrected as shown below:

On the cover sheet insert:

"I731 Assignee:

[SEAL] Lake and Development Company of Tehama County, Santa Clara,

Calif. part interest Signed and Scaled this T weary-seventh D y fDecember I977 A ttest:

RUTH C. MASON Attesting Officer LUTRELLE F. PARKER Acting Commissionerof Patents and Trademarks UNITED STATES PATENT AND TRADEMARK OFFICECERTIFICATE OF CORRECTION PATENT NO. 3,857,651

DATED December 31, 1974 INVENTOR(S) Anthony I. Bruno It is certifiedthat error appears in the above-identified patent and that said LettersPatent is hereby corrected as shown below:

Certificate of Correction issued December 27, 1977 issued in error andis hereby rescinded.

THIS CERTIFICATE SUPERSEDES CERTIFICATE OF CORRECTION ISSUED December27, 1977.

Signed and Scaled this Fifth Day of August I980 [SEAL] Attest:

SIDNEY A. DIAMOND Arresting Oflicer Commissioner of Patents andTrademarks

1. Pumping units for a cylindrical cyclonic elevator tube in which fluidunder pressure from a source thereof has communication therewith via aplurality of circumferentially spaced jet orifices set at inwardlydireCted angles gradually increasing from a minimum angle with respectto the central axis of the tube of not less than 5* andcircumferentially directed compound angles of inclinationcorrespondingly gradually decreasing in inclination from a maximum anglecircumferentially for ejecting vortically directed jets of fluid underpressure upwardly through the cyclonic elevator to effect transportationof comminuted and/or fluid material through such tube; each said pumpingunit comprising in combination: a. a tubular section having an axiallength substantially equal to its radius; b. a frusto-conical sectionhaving its truncated end secured to the lower end of said tubularsection and its flared sides extending therefrom a distance comparableto the length of said tubular section; c. a transition ring having itsouter periphery secured to the flared open end on said conical sectionand an inner periphery of a diameter comparable to said tubular sectionand having such circumferentially spaced jet orifices formedtherebetween from the bottom to the upper surface thereof such that theinwardly directed angle of the minimum angle of such jet orificesconverges with a projection of the inner surface of the flared sidewalls of said conical section, slightly above the truncated end of saidconical section; d. an intermediate tubular section having a diameterequal to that of said tubular section and secured opposite thereto tothe bottom surface of said transition ring with its internal peripheryflush with the inner periphery of said transition ring; e. a manifoldfor each of said pumping units comprising an annular tube, of C-shapedcross section radially thereof and of a diameter vertically from itsannular crown to its annular tail slightly greater than the verticalthickness, top to bottom, of said transition ring and having its annularcrown secured to the outer periphery of the flared end of said conicalsection at its plane of connection to said transition ring and havingits annular tail extending horizontally toward said intermediate tubularsection and secured thereto for providing an annular chamber about theouter exposed periphery and bottom surface of said transition ring; f.and means for communicating said annular chamber with the source offluid under pressure.
 2. The combination in accordance with claim 1 inwhich the plurality of spaced jet orifices formed in said transitionring of said pumping unit have their inlet ends on the manifold side ofthe transition ring arranged equidistant from center of the latter andtheir outlet ends on the opposite side of such ring, beginning with afirst such jet orifices having its axis inclined at a minimum angleradially inward of such ring, arranged in groups progressivelydecreasing in distance radially of said transition ring in a spiralpattern toward the axis of the latter whereby said bores have their axesdisposed in progressively decreasing angles toward center in such spiralpattern.
 3. The combination in accordance with claim 1 in which thefirst named jet orifice in said transition ring has its outlet endoffset relative to its inlet end at a greater distance circumferentiallythan such offset relation of the inlet to outlet of the other orificesof said plurality thereof and in which successive groups of orificesthereof have the offset relation of their inlet and outlet graduallydiminishing in a circumferential direction progressively about thespiral pattern thereof on said transition ring.
 4. The combination inaccordance with claim 3 in which said pumping unit is modular and eachincludes means for detachably securing several such pumping units intandem arrangement concentric to the elevator tube.
 5. The combinationin accordance with that of claim 3 including at least three stages ofsaid pumping units arranged in tandem concentric to each other and tosaid cyclonic elevator tube comprising: a. a first open ended entrystage having the circumferentiAlly spaced orifices in its transitionring disposed at compound angles ranging from 8* to 27* radially andcorrespondingly 30* to 5* circumferentially; b. a second, intermediatestage having the circumferentially spaced orifices in its transitionring disposed at compound angles ranging from 9* to 10* radially andcorrespondingly 20* to 8* circumferentially; and c. an innermost stagehaving the circumferentially spaced orifices in its transition ringdisposed at compound angles ranging from 9* to 5* radially andcorrespondingly 14* to 10* circumferentially.